WO1995021359A1 - Refrigeration system and a method for regulating the refrigeration capacity of such a system - Google Patents
Refrigeration system and a method for regulating the refrigeration capacity of such a system Download PDFInfo
- Publication number
- WO1995021359A1 WO1995021359A1 PCT/SE1994/000083 SE9400083W WO9521359A1 WO 1995021359 A1 WO1995021359 A1 WO 1995021359A1 SE 9400083 W SE9400083 W SE 9400083W WO 9521359 A1 WO9521359 A1 WO 9521359A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- economizer
- refrigerant
- compressor
- channel
- channel means
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
Definitions
- Refrigeration system and a method for regulating the refrigeration capacity of such a system.
- the present invention in a first aspect relates to a refrigeration system having a rotary screw compressor, a condenser, first pressure reducing means, an economizer, second pressure reducing means and an evaporator, which elements are connected by channel means in the mentioned sequence and by channel means connecting the evaporator to a low pressure inlet of the compressor port to form a closed loop for a refrigerant and further having economizer channel means selectively connecting the economizer to a closed working chamber of the compressor and adjustable valve means in the economizer channel means.
- an economizer is frequently applied in order to increase the refrigeration capacity of a refrigeration system.
- a part of the refrigerant is withdrawn from the main loop and is evaporated.
- the refrigerant evaporated in the economizer is then led to a closed working chamber of the compressor at an intermediate pressure level.
- the heat required for evaporating the ref ⁇ gerant is taken from the remaining refrigerant in the main loop, which thereby is subcooled. This is done in a heat exchanger or in a flash tank.
- the components of the system, in particular the compressor thus can be made smaller and consequently less expensive to manufacture.
- the refrigeration demand may vary widely, which makes it desirable to vary the refrigeration capacity correspondingly.
- This can be accomplished in various ways; by measures directly affecting the operation of the compressor, by measures affecting the conditions of the flow of refrigerant through the evaporator or by a combination of such measures.
- the main concept of the invention concerns regulating by means affecting the conditions of the flow of refrigerant through the evaporator.
- Examples of such systems are disclosed in US-A 2 388 556, US-A 4 899 555, US-A 4 947 655, US-A 5 062 274 and US-A 5 095 712.
- the regulation is accomplished in that the flow of refrigerant withdrawn from the main loop is regulated before it enters the economizer when it still is in the liquid state.
- the object of the present invention is to attain a new regulation system for the refrigeration capacity which is more simple and reliable.
- a refrigeration system of the kind in question has continuously adjustable valve means for regulating the mass flow of gaseous refrigerant through the economizer channel means, which adjustable valve means are governed by sensing means sensing the value of at least one parameter of the refrigerant in the closed loop, which parameter is indicative of the required refrigeration capacity.
- valve means in the channel from the economizer to the compressor is not novel as such.
- US-A 4 899 555 and US-A 4 947 655 as well as in US-A 3 827 250, US-A 4 727 725 and US-A 4 748 831 valve means are provided in that channel, but in none of the disclosures the valve means are governed by sensing means in the main loop and none are used for regulating the refrigeration capacity of the system.
- the compressor also has return channel means for varying the compressor capacity, in which case the adjustable valve means also can control the flow through the return channel.
- the sensed parameter is the temperature of the refrigerant leaving the evaporator.
- Figure 1 is a block diagram of a refrigeration system according to the invention.
- FIG. 2 is a schematic view of the valve means used in the refrigeration system according to the invention.
- Figures 2a to d are simplified views of the valve means of figure 2, illustrating different valve positions.
- Figure 3 is a graph illustrating the refrigeration capacity as a function of the valve position.
- the refrigeration system illustrated in figure 1 includes a rotary screw compressor 1 1, a condenser 12, first pressure reducing means 13, an economizer 14 of the flash tank type, second pressure reducing means 15 and an evaporator 16 connected to a closed loop by channels 18, 19, 20 and 21.
- the upper part of the flash tank 14 containing gaseous refrigerant 26 is by an economizer channel 22, 23 connected to an intermediate pressure port 27 in the compressor 11.
- the intermediate pressure port 27 faces a closed working chamber of the compressor, i.e. the chamber is sealed off from communication with the inlet as well as the outlet of the compressor.
- the flow of gaseous refrigerant from the economizer 14 to the compressor 11 is regulated by a valve 17 in the economizer channel 22, 23, which valve is governed by temperature sensing means 28 sensing the temperature of the refrigerant in the outlet channel 21 from the evaporator 16.
- figure 1 is a block diagram illustrating the principle of the invention, it is to be understood that the valve 17 not necessary is located in channels outside the compressor.
- the valve thus advantageously can be arranged within the casing structure of the compressor.
- refrigerant compressed by the compressor flows through channel 18 to the condenser where the refrigerant is condensed by removing heat therefrom. From the condenser 12 the refrigerant flows through a pressure reduction valve 13 to the flash chamber 14. In the flash chamber 14 a part of the refrigerant is evaporated due to the decreased pressure, taking the evaporation heat from the remaining liquid refrigerant 25 gathered in the bottom of the flash tank 14. The thus subcooled refrigerant flows through the pressure reduc ⁇ ing valve 15 to the evaporator 16 where it is evaporated by taking up heat. The evaporated refrigerant then flows through channel 21 to the compressor low pressure inlet to be re- compressed.
- the flash gas 26 generated in the flash tank 14 flows through the economizer channel 22, 23 and the valve means 17 to the intermediate pressure port 27 in the compressor for recompression.
- the subcooling of the refrigerant in the flash tank 14 attained by such an economizer coupling increases refrigeration capacity of the evaporator 16, i.e. a larger enthalpy difference across the evaporator 16 is available.
- the increase in enthalpy difference attained by the economizer is a function of the amount of heat withdrawn from the liquid refrigerant by the refrigerant evaporated in the flash tank 14 and thus depends of the amount of gaseous refrigerant flowing through the economizer channel 22, 23 to the compressor.
- the mass flow through the economizer channel 22, 23 is regulated by a valve 17.
- the valve 17 is governed by a temperature sensing device 28 sensing the temperature Te of the refrigerant in the channel 21 connecting the evaporator to the compressor. This temperature is dependent on the heat taken up by the ref ⁇ gerant in the evaporator and thus is indicative of the demand of refrigeration capacity. Increasing Te means that higher refrigeration capacity is required and affects the valve 17 to move towards a more open position admitting a larger quantity of refrigerant to flow through the economizer channel 22, 23.
- the system thus adapts to the higher refrigeration demand since the larger mass flow of refrigerant through the economizer channel 22, 23 increases the enthalpy difference.
- Te decreases indicating a lower refrigeration demand the valve will act in the opposite direction.
- the refrigeration capacity thus can be regulated within a range, the lower limit of which is the refrigeration capacity when the valve is fully close, i.e. the economizer is de ⁇ activated and the upper limit of which is the refrigeration capacity when the valve 17 is completely open, making use of the economizer effect to its full extent.
- Te the pressure of the refrigerant at the outlet of the evaporator can be used, or a combination of these two.
- the system can be combined with direct compressor capacity regulation by means of a return channel 23, 24, through which a closed working chamber of the compressor can be brought in communication with the compressor inlet.
- a part 23 of the return channel 23, 24 is common with the economizer channel 22, 23 as can be seen in the figure.
- the intermediate pressure opening 27 of the compressor is thus common for both channels and has the dual function of either being an inlet port for the economizer channel 22, 23 or an outlet port for the return channel 23, 24.
- the return channel 23, 24 is closed by the valve 17 as long as the latter keeps the economizer channel open, whereby the refrigeration capacity solely is regulated by regulating the economizer flow.
- the valve 17 has closed the flow through the economizer channel as described above. Further reduction of the refrigeration demand will affect the valve 17 to open communication between a closed working chamber of the compressor and the compressor inlet, but the economizer channel 22, 23 will remain closed.
- the valve 17 is arranged to regulate the return flow to the compressor inlet continuously by gradually increasing the flow through the return channel. At its full open position the return flow is large enough to bring down the pressure in the closed chamber to equal the inlet pressure so that the actual compression takes place only downstream the intermediate pressure port 27.
- valve 17 In figure 2 the function of the valve 17 i schematically illustrated.
- the valve is shown in the position where the system operates at full refrigeration capacity, in which the flow of gaseous refrigerant from the economizer through channel 22 to the compressor through channel 23 is unrestricted, whereas the valve body 32 closes communication between the return channel 24 connected to compressor inlet and the channels 22, 23.
- the restriction of the flow of refrigerant from channel 22 to channel 23 will gradually increase which means a decrease in the economizer effect.
- FIGs 2a to d illustrate further different positions of the valve body 32, representing various degrees of reduction in refrigeration capacity.
- the valve body 32 has moved up ⁇ wards from the position of figure 2 and restricts the flow through the economizer channel 22, 23 so that a reduction of refrigeration capacity is attained by reducing the economizer effect.
- the valve body 32 is in the position where the economizer channel 22, 23 is closed, which represents the maximum capacity reduction that can be attained by the economizer regulation.
- the return channel 23, 24 is in principle kept closed by the valve body 32 which means that the compressor operates at nominal capacity.
- a leakage communication is established between channel part 23 and the return channel 24 in order to avoid a valve position where channel part 23 is completely closed, which would negatively affect the operation of the compressor.
- valve body 32 is moved by an actuating unit 30 through the valve rod 31, which actuat ⁇ ing movement is governed by signals transmitted through the signalling circuit 29 from the sensing device 28, sensing the temperature in the evaporator outlet as described above.
- the regulation range can be still further extended beyond the lower limit by additional valve means, through which a restricted communication between the economizer and the compressor inlet can be established.
- Such a modification can be made by admitting upwards movement of the valve body 32 beyond the position in figure 2d and design the connection to channel 22 with tapering decreasing diameter towards the junction with channel 23.
- the regulation is further illustrated by the graph in figure 3 showing the refrigeration capacity in percentage of full capacity as a function of the position of the valve body 32, where s is the distance from the bottom position of the valve shown in figure 2.
- line A represents the economizer regulation covering the upper range between 75 and 100 % of full capacity
- line B the compressor regulation covering the lower range between 40 and 75 % of full capacity.
- Points a to d represent the valve positions in figures a to d.
- Line C represents the additional regulation range down to 25 % that can be attained by connecting the economizer to compressor inlet.
- the refrigeration capacity of a refrigeration system can be regulated continuously in a simple and reliable way by gradually restricting the flow of refrigerant through the economizer channel to the compressor, thereby regulating the enthalpy difference attained by the economizer coupling, and in applications where a larger regulation range is required, further by gradually opening the compressor return flow, thereby reducing the compressor capacity.
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/SE1994/000083 WO1995021359A1 (en) | 1994-02-03 | 1994-02-03 | Refrigeration system and a method for regulating the refrigeration capacity of such a system |
EP94910073A EP0741851B1 (en) | 1994-02-03 | 1994-02-03 | Refrigeration system and a method for regulating the refrigeration capacity of such a system |
JP7520532A JPH10510906A (en) | 1994-02-03 | 1994-02-03 | Cooling system and cooling capacity control method for cooling system |
US08/669,442 US5816055A (en) | 1994-02-03 | 1994-02-03 | Refrigeration system anad a method for regulating the refrigeration capacity of such a system |
DE69414415T DE69414415T2 (en) | 1994-02-03 | 1994-02-03 | REFRIGERATION SYSTEM AND METHOD FOR CONTROLLING THE REFRIGERATION PERFORMANCE OF SUCH A SYSTEM |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/SE1994/000083 WO1995021359A1 (en) | 1994-02-03 | 1994-02-03 | Refrigeration system and a method for regulating the refrigeration capacity of such a system |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1995021359A1 true WO1995021359A1 (en) | 1995-08-10 |
Family
ID=20392556
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/SE1994/000083 WO1995021359A1 (en) | 1994-02-03 | 1994-02-03 | Refrigeration system and a method for regulating the refrigeration capacity of such a system |
Country Status (5)
Country | Link |
---|---|
US (1) | US5816055A (en) |
EP (1) | EP0741851B1 (en) |
JP (1) | JPH10510906A (en) |
DE (1) | DE69414415T2 (en) |
WO (1) | WO1995021359A1 (en) |
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EP0972942A2 (en) * | 1998-07-13 | 2000-01-19 | Carrier Corporation | Scroll compressor with unloader valve between economizer and suction |
EP0976994A1 (en) * | 1997-11-21 | 2000-02-02 | Daikin Industries, Ltd. | Refrigerator and method of filling it with coolant |
WO2004099684A2 (en) * | 2003-05-05 | 2004-11-18 | Carrier Corporation | Vapor compression system |
WO2006015629A1 (en) * | 2004-08-09 | 2006-02-16 | Carrier Corporation | Flashgas removal from a receiver in a refrigeration circuit |
CN100410596C (en) * | 2005-05-27 | 2008-08-13 | 株式会社神户制钢所 | Auger-type refrigerating plant |
EP2165124A1 (en) * | 2007-05-14 | 2010-03-24 | Carrier Corporation | Refrigerant vapor compression system with flash tank economizer |
CN104697226A (en) * | 2015-03-17 | 2015-06-10 | 浙江国祥空调设备有限公司 | Evaporation condensation water chilling unit with free cooling device |
US10088206B2 (en) | 2013-10-17 | 2018-10-02 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
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US6093007A (en) * | 1995-10-30 | 2000-07-25 | Shaw; David N. | Multi-rotor helical-screw compressor with thrust balance device |
US6105378A (en) * | 1995-10-30 | 2000-08-22 | Shaw; David N. | Variable capacity vapor compression cooling system |
US6206652B1 (en) | 1998-08-25 | 2001-03-27 | Copeland Corporation | Compressor capacity modulation |
US6047556A (en) * | 1997-12-08 | 2000-04-11 | Carrier Corporation | Pulsed flow for capacity control |
US6141980A (en) * | 1998-02-05 | 2000-11-07 | Shaw; David N. | Evaporator generated foam control of compression systems |
US6186758B1 (en) | 1998-02-13 | 2001-02-13 | David N. Shaw | Multi-rotor helical-screw compressor with discharge side thrust balance device |
KR19990081638A (en) * | 1998-04-30 | 1999-11-15 | 윤종용 | Multi type air conditioner and control method |
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US6718781B2 (en) | 2001-07-11 | 2004-04-13 | Thermo King Corporation | Refrigeration unit apparatus and method |
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US6973797B2 (en) * | 2004-05-10 | 2005-12-13 | York International Corporation | Capacity control for economizer refrigeration systems |
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US11629894B2 (en) * | 2020-01-10 | 2023-04-18 | Johnson Controls Tyco IP Holdings LLP | Economizer control systems and methods |
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- 1994-02-03 EP EP94910073A patent/EP0741851B1/en not_active Expired - Lifetime
- 1994-02-03 JP JP7520532A patent/JPH10510906A/en active Pending
- 1994-02-03 WO PCT/SE1994/000083 patent/WO1995021359A1/en active IP Right Grant
- 1994-02-03 US US08/669,442 patent/US5816055A/en not_active Expired - Fee Related
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Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0976994A1 (en) * | 1997-11-21 | 2000-02-02 | Daikin Industries, Ltd. | Refrigerator and method of filling it with coolant |
EP0976994A4 (en) * | 1997-11-21 | 2000-03-15 | Daikin Ind Ltd | Refrigerator and method of filling it with coolant |
US6233961B1 (en) | 1997-11-21 | 2001-05-22 | Daikin Industries, Ltd. | Refrigerator and method of filling it with coolant |
EP0972942A2 (en) * | 1998-07-13 | 2000-01-19 | Carrier Corporation | Scroll compressor with unloader valve between economizer and suction |
EP0972942A3 (en) * | 1998-07-13 | 2001-08-08 | Carrier Corporation | Scroll compressor with unloader valve between economizer and suction |
WO2004099684A3 (en) * | 2003-05-05 | 2005-02-03 | Carrier Corp | Vapor compression system |
WO2004099684A2 (en) * | 2003-05-05 | 2004-11-18 | Carrier Corporation | Vapor compression system |
US7201008B2 (en) | 2003-05-05 | 2007-04-10 | Carrier Corporation | Vapor compression system performance enhancement and discharge temperature reduction in the unloaded mode of operation |
WO2006015629A1 (en) * | 2004-08-09 | 2006-02-16 | Carrier Corporation | Flashgas removal from a receiver in a refrigeration circuit |
CN100410596C (en) * | 2005-05-27 | 2008-08-13 | 株式会社神户制钢所 | Auger-type refrigerating plant |
EP2165124A1 (en) * | 2007-05-14 | 2010-03-24 | Carrier Corporation | Refrigerant vapor compression system with flash tank economizer |
EP2165124A4 (en) * | 2007-05-14 | 2013-05-29 | Carrier Corp | Refrigerant vapor compression system with flash tank economizer |
US8671703B2 (en) | 2007-05-14 | 2014-03-18 | Carrier Corporation | Refrigerant vapor compression system with flash tank economizer |
US10088206B2 (en) | 2013-10-17 | 2018-10-02 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
CN104697226A (en) * | 2015-03-17 | 2015-06-10 | 浙江国祥空调设备有限公司 | Evaporation condensation water chilling unit with free cooling device |
Also Published As
Publication number | Publication date |
---|---|
JPH10510906A (en) | 1998-10-20 |
EP0741851A1 (en) | 1996-11-13 |
DE69414415D1 (en) | 1998-12-10 |
DE69414415T2 (en) | 1999-06-10 |
US5816055A (en) | 1998-10-06 |
EP0741851B1 (en) | 1998-11-04 |
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